US10830240B2 - Magnetic drive pump - Google Patents

Magnetic drive pump Download PDF

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Publication number
US10830240B2
US10830240B2 US16/087,110 US201716087110A US10830240B2 US 10830240 B2 US10830240 B2 US 10830240B2 US 201716087110 A US201716087110 A US 201716087110A US 10830240 B2 US10830240 B2 US 10830240B2
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United States
Prior art keywords
bearing
chamber
impeller
pump
magnetic drive
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Active, expires
Application number
US16/087,110
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English (en)
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US20190113038A1 (en
Inventor
Thomas Eschner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Klaus Union GmbH and Co KG
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Klaus Union GmbH and Co KG
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Assigned to KLAUS UNION GMBH & CO. KG reassignment KLAUS UNION GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ESCHNER, THOMAS
Assigned to KLAUS UNION GMBH & CO. KG reassignment KLAUS UNION GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ESCHNER, THOMAS
Publication of US20190113038A1 publication Critical patent/US20190113038A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/025—Details of the can separating the pump and drive area
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/026—Details of the bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/027—Details of the magnetic circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/06—Lubrication
    • F04D29/061—Lubrication especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/106—Shaft sealings especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps

Definitions

  • the invention relates to a magnetic drive pump.
  • Magnetic drive pumps have been known from the prior art for a long time.
  • Magnetic drive pumps utilize the attractive and repulsive forces between permanent magnets in both coupling halves for contactless and slip-free torque transmission.
  • the drive power is transmitted in a contactless and slip-free manner from an electric motor via a drive shaft, which is connected to an outer rotor, to a rotor which bears pump-side magnets (inner rotor).
  • the rotor drives an impeller via a pump shaft.
  • the pump shaft in this case is supported in the housing of the pump by a bearing which is lubricated by the conveyed fluid.
  • a can is arranged between the two rotors. The can separates the conveyed fluid from the environment.
  • the conveyed fluid in magnetic drive pumps is thus separated from the environment exclusively by means of static seals, so that the conveyed fluid is prevented particularly safely from leaking into the environment. Therefore, magnetic drive pumps are frequently used in the chemical and petrochemical sector.
  • the bearing is lubricated in magnetic drive pumps by the conveyed fluid of the pump, with a partial flow of the conveyed fluid which is necessary to that end being taken from the impeller chamber at a point of high pressure, passing through the bearing to be lubricated and arriving via the bearing in the impeller chamber and in the coupling chamber which is enclosed by the can.
  • the conveyed fluid is recirculated into the impeller chamber via a drainage bore which connects the coupling chamber to a point of low pressure in the impeller chamber.
  • the conveyed fluid exiting into the coupling chamber via the bearing at the same time cools the can and dissipates the heat produced there by eddy currents.
  • a magnetic drive pump according to the invention comprises:
  • the coupling chamber is closed in (virtually) fluid-tight manner relative to the impeller chamber.
  • the magnetic drive pump according to the invention has the advantage over the prior art that sufficient lubrication of the bearing is also ensured over a longer period when the pump is operating in dry-run condition and no further conveyed fluid can be conveyed through the duct to the bearing.
  • the coupling chamber is closed in fluid-tight manner relative to the impeller chamber, i.e. at most a slight recirculation of the conveyed fluid out of the coupling chamber directly into the impeller chamber takes place, the conveyed fluid flows significantly more slowly out of the region of the bearing.
  • the bearing remains sufficiently lubricated over a considerably longer period, even if no conveyed fluid is replenished via the duct.
  • the conveyed fluid arrives not only in the coupling chamber, but also in the impeller chamber, via the bearing.
  • the conveyed fluid therefore arrives back in the impeller chamber even without the draining which conventionally takes place from the coupling chamber, so that circulation of the conveyed fluid which serves as a lubricant is ensured during normal operation of the pump according to the invention.
  • the conveyed fluid which exits into the impeller chamber via the bearing is replenished from the coupling chamber.
  • the conveyed fluid present in the coupling chamber is sufficient to maintain the lubrication over a longer period (up to one hour or even longer) until it is noticed that the pump is in dry-run condition and the pump is switched off.
  • the can consists of a non-metallic material. Owing to the lack of electrical conductivity of the non-metallic material, eddy-current losses are avoided, as a result of which the efficiency of the magnetic drive pump increases significantly. In particular, unlike in the prior art, no cooling of the can by the conveyed fluid is necessary. The reduced circulation of the conveyed fluid caused by the closure according to the invention of the coupling chamber relative to the impeller chamber is thus unproblematic with regard to the cooling in combination with the non-metallic material of the can.
  • the can consists of engineering ceramic or plastics, such as for example PEEK. Cans made of plastics are characterized by their low weight and their low fragility and ease of handling. Cans made of ceramic (e.g. SiC) have great pressure resistance and excellent heat resistance.
  • At least one restriction element is provided which restricts the throughflow of the conveyed fluid through the duct.
  • the restriction element may to this end cover or close e.g. the input-side opening of the duct to the impeller chamber.
  • the restriction element may be formed e.g. in a disc shape and be fastened to the ring, so that it partially covers the opening of the duct.
  • a ring disc fastened to the ring can form the restriction element and at the same time closes a drainage bore formed in the ring which is originally provided to connect the coupling chamber to the impeller chamber.
  • the parts of a conventional magnetic drive pump can be used at low cost for a pump configured according to the invention.
  • the additional ring disc preferably in combination with the use of a non-metallic can.
  • the ring disc partially closes the duct in order to reduce the cross-section to restrict the flow of fluid, and completely closes the drainage bore.
  • the restriction element is arranged in the inflow, so that the throughflow of the conveyed fluid through the duct is restricted.
  • the restriction element to this end is embodied such that particles have to move radially inwards into the duct against the centrifugal force in order to enter the coupling chamber.
  • the partial flow of the conveyed fluid which enters the coupling chamber out of the impeller chamber to the bearing for the purpose of lubricating the bearing is considerably reduced by the restriction element, as a result of which the introduction of particles into the can in the event of the flow of fluid being laden with solids is reduced.
  • the pump shaft does not have a fluidic connection between the impeller chamber and coupling chamber.
  • the pump shaft comprises an axial through-bore in order to ensure sufficient circulation of the conveyed fluid from the pressure side of the impeller chamber via the bearing into the coupling chamber, and through the pump shaft back to the suction side of the impeller chamber for the purpose of sufficient cooling of the can. Owing to the lack of a fluidic connection via the pump shaft, the circulation is reduced according to the invention, and as a result the coupling chamber remains filled with conveyed fluid over as long a period as possible in dry-run condition in order to maintain the lubrication.
  • the pump shaft may be formed as a solid body. It is however also possible for the pump shaft to be formed as a hollow shaft which is closed at least at one end.
  • One preferred embodiment provides for recirculation of the conveyed fluid out of the coupling chamber into the impeller chamber to take place via the bearing.
  • the recirculation of the conveyed fluid out of the coupling chamber into the impeller chamber preferably takes place exclusively via the bearing.
  • the recirculation of the conveyed fluid out of the coupling chamber into the impeller chamber takes place in the region of the bearing, so that the bearing is sufficiently lubricated over a considerably longer period, even if no conveyed fluid is replenished via the duct.
  • the conveyed fluid therefore re-arrives in the impeller chamber, so that circulation of the conveyed fluid, which serves as lubricant, during normal operation of the pump according to the invention is ensured.
  • the conveyed fluid which emerges into the impeller chamber via the bearing is replenished from the coupling chamber.
  • the conveyed fluid present in the coupling chamber is sufficient to maintain the lubrication over a longer period (up to one hour or even longer).
  • the pump can be switched off without damage as soon as it is noticed that the pump is in dry-run condition.
  • a radial bearing gap in the bearing.
  • the radial bearing gap is preferably located between the bearing elements of the bearing, so that lubrication is ensured even when the pump is in dry-run condition.
  • a further advantageous embodiment is that the radial bearing gap is arranged on the impeller side in the bearing.
  • the radial bearing gap restricts the recirculation of the conveyed fluid out of the coupling chamber into the impeller chamber.
  • the radial bearing gap in the impeller-side radial bearing of the bearing preferably does not have a lubrication groove, in order to restrict the recirculation of the conveyed fluid further. Since flushing of the bearing in the event of the conveyed fluid being laden with solids thereby does not occur, the introduction of particles into the coupling chamber through the restriction element described above and below should be reduced.
  • the embodiment, in which lubrication grooves are arranged on the coupling side in the bearing is particularly advantageous.
  • the coupling-side radial bearing of the bearing may comprise lubrication grooves through which flushing between the bearing elements is ensured. This is of significant importance in the event of the conveyed fluid being laden with solids in order nevertheless to ensure great longevity of the bearing.
  • FIGURES show a particularly preferred variant embodiment of the invention.
  • the invention is however not limited to the variant embodiment shown.
  • the invention in so far as it is technically reasonable, covers any combinations whatsoever of the technical features which are outlined in the claims or are described in the description as being relevant to the invention.
  • FIGURES show in:
  • FIG. 1 a sectional view of a magnetic drive pump according to the invention.
  • FIG. 1 shows a magnetic drive pump 10 according to the invention in one possible configuration.
  • the magnetic coupling comprises a housing 12 with a ring 16 .
  • the housing 12 includes an impeller chamber 14 for receiving a conveyed fluid which is drawn in through an inlet 44 and is ejected through an outlet 46 .
  • the pump 10 comprises a can 18 , wherein the can 18 and the ring 16 enclose a coupling chamber 20 .
  • the ring 16 separates the coupling chamber 20 from the impeller chamber 14 .
  • the can 18 consists of a non-metallic material, so that no heat generation due to eddy currents occurs therein.
  • a pump shaft 22 extends from the impeller chamber 14 through a central opening provided in the ring 16 into the coupling chamber 20 .
  • An impeller 24 is fastened to the pump shaft 22 .
  • a rotor 50 equipped with permanent magnets is arranged in the coupling chamber 20 .
  • the pump 10 has a bearing 26 , e.g. in the form of a plain bearing with ceramic bearing elements, which is supported by the ring 16 .
  • a duct 28 for supplying a partial flow of the conveyed fluid from the impeller chamber 14 to the bearing 26 is provided in the ring 16 for the purpose of lubrication.
  • the ring 16 comprises a drainage bore 30 which is originally provided for draining the coupling chamber 20 into the impeller chamber 14 .
  • the opening of the drainage bore 30 facing the impeller chamber 14 is closed by means of a disc-shaped element 32 .
  • the coupling chamber 20 is closed in fluid-tight manner relative to the impeller chamber 14 . In this manner, it is ensured that a sufficient quantity of conveyed fluid for lubricating the bearing 26 in dry-run condition remains in the coupling chamber 20 over a certain time. Recirculation of the conveyed fluid out of the coupling chamber 20 into the impeller chamber 14 takes place via the bearing 26 . The exclusive recirculation of the conveyed fluid via the bearing 26 out of the coupling chamber 20 into the impeller chamber 14 provides a sufficient quantity of conveyed fluid for lubricating the bearing 26 over a longer period.
  • the disc-shaped element 32 is fastened to the ring 16 by means of a screw 40 .
  • the recirculation of the conveyed fluid out of the coupling chamber 20 into the impeller chamber 14 therefore takes place via a radial bearing gap 52 in the bearing 26 .
  • the radial bearing gap 52 is arranged between the bearing elements of the impeller-side radial bearing 26 b of the bearing 26 , which ensures lubrication between the bearing elements even when the pump is in dry-run condition.
  • the radial bearing gap 52 restricts the recirculation of the conveyed fluid out of the coupling chamber 20 into the impeller chamber 14 .
  • the impeller-side radial bearing 26 b of the bearing 26 does not comprise a lubrication groove, in order to restrict the recirculation of the conveyed fluid.
  • a lubrication groove 54 can be discerned which ensures sufficient flushing between the bearing elements.
  • the impeller 24 comprises a hollow-cylindrical portion 42 which extends in the axial direction of the pump shaft 22 and adjoins the disc-shaped element 32 .
  • a restriction element 34 which is arranged between the impeller chamber 14 and the opening 36 of the duct 28 is provided.
  • the restriction element 34 prevents any accumulation of particles in the coupling chamber in the event of the flow of fluid being laden with solids.
  • the restriction element 34 restricts the throughflow of the conveyed fluid through the duct 28 .
  • the restriction element 34 is formed on the disc-shaped element 32 and covers the duct opening 36 .
  • the restriction element 34 rests against the duct opening 36 such that the conveyed fluid can flow into the region between the restriction element 34 and duct opening 36 .
  • the restriction element 34 comprises on its outer circumference a chamfer 38 which is arranged on the side of the element 32 remote from the impeller 24 .
  • a gap 48 through which conveyed fluid can flow into the duct 28 is produced between the restriction element 34 and ring 16 .
  • the restriction element 34 in this manner effects that particles to have to move radially inwards into the duct 28 against the centrifugal force, in order to enter the coupling chamber 20 .
  • the partial flow of the conveyed fluid which arrives in the coupling chamber out of the impeller chamber 14 to the bearing 26 for the purpose of lubricating the bearing 26 is considerably reduced by the restriction element 34 , as a result of which the introduction of particles into the can 18 in the event of the flow of fluid being laden with solids is reduced.
  • the restriction element 34 in this manner restricts the flow of conveyed fluid through the duct 28 .
  • the pump shaft 22 of the magnetic drive pump 10 is formed such that it does not produce a fluidic connection between the coupling chamber 20 and the impeller chamber 14 . To this end, the pump shaft 22 is formed as a solid body.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US16/087,110 2016-03-22 2017-03-22 Magnetic drive pump Active 2037-08-30 US10830240B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102016105309.0A DE102016105309A1 (de) 2016-03-22 2016-03-22 Magnetkupplungspumpe
DE102016105309.0 2016-03-22
DE102016105309 2016-03-22
PCT/EP2017/056881 WO2017162775A1 (fr) 2016-03-22 2017-03-22 Pompe à entraînement magnétique

Publications (2)

Publication Number Publication Date
US20190113038A1 US20190113038A1 (en) 2019-04-18
US10830240B2 true US10830240B2 (en) 2020-11-10

Family

ID=58548657

Family Applications (1)

Application Number Title Priority Date Filing Date
US16/087,110 Active 2037-08-30 US10830240B2 (en) 2016-03-22 2017-03-22 Magnetic drive pump

Country Status (7)

Country Link
US (1) US10830240B2 (fr)
EP (1) EP3433496B1 (fr)
CN (1) CN109072927B (fr)
DE (1) DE102016105309A1 (fr)
ES (1) ES2911510T3 (fr)
RU (1) RU2746491C2 (fr)
WO (1) WO2017162775A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017206089B4 (de) * 2017-04-10 2020-01-16 BSH Hausgeräte GmbH Nassläufer-Pumpe und Haushaltsgerät
WO2019237689A1 (fr) * 2018-06-15 2019-12-19 广东威灵电机制造有限公司 Ensemble pompe et lave-vaisselle
GB2581339A (en) * 2019-02-08 2020-08-19 Hmd Seal/Less Pumps Ltd Containment shell for a magnetic pump
DE102019002392A1 (de) 2019-04-02 2020-10-08 KSB SE & Co. KGaA Wärmesperre
CN110410334A (zh) * 2019-06-29 2019-11-05 浙江威肯特智能机械有限公司 一种沥青泵
DE102019005095A1 (de) * 2019-07-23 2021-01-28 KSB SE & Co. KGaA Pumpenanordnung mit einem Schmier- und Kühlsystem
CN110848260B (zh) * 2019-11-18 2021-01-12 上海凯士比泵有限公司 一种用于滑动轴承上的自润滑系统
CN110748491B (zh) * 2019-12-11 2024-05-14 杨华标 物联智能磁电驱动泵
CN116498593B (zh) * 2023-05-11 2024-05-24 甘肃莱德尔流体节能科技开发有限公司 一种可空载可输送含颗粒和少量气体的三相流磁力泵
CN117386633B (zh) * 2023-12-12 2024-03-01 烟台恒邦泵业有限公司 一种无泄漏磁力旋转喷射泵

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GB1069896A (en) * 1963-05-15 1967-05-24 Jean Louis Stulens Improvements in or relating to impeller pumps,particularly for use in central heating installations
DE3622269A1 (de) * 1986-07-03 1988-01-14 Richard Halm Spaltrohrmotorpumpe
US4808087A (en) * 1982-09-28 1989-02-28 Nikkiso Co., Ltd. Canned motor pump
DE4009199A1 (de) 1990-03-22 1991-09-26 Rheinhuette Gmbh & Co Trockenlaufsicherung fuer magnetkupplungspumpen
US5256038A (en) * 1991-11-12 1993-10-26 Sundstrand Corp. Canned motor pump
US5397220A (en) * 1993-03-18 1995-03-14 Nippon Shokubai Co., Ltd. Canned motor pump
EP0814275A2 (fr) 1996-06-20 1997-12-29 Franz Klaus Union Armaturen Pumpen GmbH & Co. Palier lisse hydrodynamique pour le rotor d'une pompe
US20010043871A1 (en) 2000-05-22 2001-11-22 Itt Richter Chemie-Technik Gmbh Magnetically coupled canned rotary pump
US20090035161A1 (en) * 2005-09-24 2009-02-05 Grundfos Management A/S Pump assembly
US20160177962A1 (en) * 2013-07-25 2016-06-23 Xylem Ip Holdings Llc Circulating pump
US20170122324A1 (en) * 2015-11-02 2017-05-04 Sulzer Management Ag Pump drive unit for conveying a process fluid

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JPS54100503A (en) * 1978-01-25 1979-08-08 Hitachi Ltd Pump
DE3513832A1 (de) * 1985-04-17 1986-10-23 Stuebbe Asv Gmbh Kreiseleintauchpumpe
DE3943273C2 (de) * 1989-12-29 1996-07-18 Klaus Union Armaturen Horizontal angeordnete Kreiselpumpe mit Spaltrohrmagnetkupplung
RU2018717C1 (ru) * 1991-05-06 1994-08-30 Нагула Петр Константинович Герметичный насосный агрегат
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DE102013008795B3 (de) * 2013-05-24 2014-08-21 Ksb Aktiengesellschaft Pumpenanordnung

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Publication number Priority date Publication date Assignee Title
GB1069896A (en) * 1963-05-15 1967-05-24 Jean Louis Stulens Improvements in or relating to impeller pumps,particularly for use in central heating installations
US4808087A (en) * 1982-09-28 1989-02-28 Nikkiso Co., Ltd. Canned motor pump
DE3622269A1 (de) * 1986-07-03 1988-01-14 Richard Halm Spaltrohrmotorpumpe
DE4009199A1 (de) 1990-03-22 1991-09-26 Rheinhuette Gmbh & Co Trockenlaufsicherung fuer magnetkupplungspumpen
US5256038A (en) * 1991-11-12 1993-10-26 Sundstrand Corp. Canned motor pump
US5397220A (en) * 1993-03-18 1995-03-14 Nippon Shokubai Co., Ltd. Canned motor pump
EP0814275A2 (fr) 1996-06-20 1997-12-29 Franz Klaus Union Armaturen Pumpen GmbH & Co. Palier lisse hydrodynamique pour le rotor d'une pompe
US20010043871A1 (en) 2000-05-22 2001-11-22 Itt Richter Chemie-Technik Gmbh Magnetically coupled canned rotary pump
US6457951B2 (en) * 2000-05-22 2002-10-01 Itt Richter Chemie-Technik Gmbh Magnetically coupled canned rotary pump
US20090035161A1 (en) * 2005-09-24 2009-02-05 Grundfos Management A/S Pump assembly
US20160177962A1 (en) * 2013-07-25 2016-06-23 Xylem Ip Holdings Llc Circulating pump
US20170122324A1 (en) * 2015-11-02 2017-05-04 Sulzer Management Ag Pump drive unit for conveying a process fluid

Non-Patent Citations (1)

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Title
Internationaler Recherchenbericht und der Schriftliche Bescheid [International Search Report and the Written Opinion] dated Jul. 26, 2017 From the Internationalen Recherchenbehörde [International Searching Authority] Re. Application No. PCT/EP2017/056881 and its Translation of Search Report Into English. (13 Pages).

Also Published As

Publication number Publication date
CN109072927B (zh) 2021-03-12
RU2746491C2 (ru) 2021-04-14
EP3433496B1 (fr) 2022-01-26
WO2017162775A1 (fr) 2017-09-28
RU2018136882A (ru) 2020-04-22
EP3433496A1 (fr) 2019-01-30
RU2018136882A3 (fr) 2020-06-23
CN109072927A (zh) 2018-12-21
DE102016105309A1 (de) 2017-09-28
US20190113038A1 (en) 2019-04-18
ES2911510T3 (es) 2022-05-19

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